US6394928B1 - Automatic transmission powertrain - Google Patents

Automatic transmission powertrain Download PDF

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Publication number
US6394928B1
US6394928B1 US09/610,898 US61089800A US6394928B1 US 6394928 B1 US6394928 B1 US 6394928B1 US 61089800 A US61089800 A US 61089800A US 6394928 B1 US6394928 B1 US 6394928B1
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Prior art keywords
planetary gearset
shaft
power transmitting
powertrain
gear
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Expired - Fee Related, expires
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US09/610,898
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English (en)
Inventor
Jong-sool Park
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Hyundai Motor Co
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Hyundai Motor Co
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H47/00—Combinations of mechanical gearing with fluid clutches or fluid gearing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/62—Gearings having three or more central gears
    • F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/0008—Transmissions for multiple ratios specially adapted for front-wheel-driven vehicles
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0043—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising four forward speeds

Definitions

  • the present invention relates to an automatic transmission powertrain. More particularly, the present invention relates to an automatic transmission powertrain in which two single pinion planetary gearsets are combined in a simple manner to realize a primary shift portion and a secondary shift portion such that a length of the powertrain is minimized, and in which a one-way clutch is used for 1 ⁇ 2, 2 ⁇ 3 and 4 ⁇ 2 shifting, thereby greatly improving shift feel.
  • a transmission control unit included in the automatic transmission automatically controls a shift ratio according to changes in vehicle speed and load.
  • a planetary gearset is used as a multi-stage gearshift mechanism in the transmission control unit.
  • the planetary gearset generally includes an input element for receiving engine torque; an output element for transmitting the engine torque to a final reduction gear after the torque has undergone shifting; and a reaction element for enabling the engine torque received by the input element to be transmitted to the output element after being shifted to a predetermined range.
  • the output element is typically fixedly connected to the final reduction gear.
  • the input element is varied, the input element is connected to an element that transmits the engine torque with a friction element interposed therebetween.
  • the reaction element is connected to a transmission housing with a friction element interposed therebetween.
  • a powertrain can have a variety of different structures including a structure in which planet carriers are interconnected, a structure in which a common sun gear is used and a planet carrier and a ring gear are directly connected, a structure in which a planet carrier and a ring gear are directly connected, and many more.
  • the present invention provides an automatic transmission powertrain comprising a torque converter acting as a fluid link between an engine and a transmission, the torque converter outputting rotational power to an input shaft of the powertrain; a primary shift portion provided on a first shaft, a long axis of which is aligned with a long axis of the input shaft, the primary shaft portion being selectively connected to the input shaft to receive rotational power; a secondary shift portion provided on a second shaft, the second shaft being parallel to the first shaft with a predetermined gap therebetween, and the secondary shift portion being connected to the primary shift portion via two power transmitting paths to transmit power to an output shaft of the powertrain; a power transmitting means for transmitting rotational power of the primary shift portion to the secondary shift portion; a brake means for operating operational elements of the primary shift portion and the secondary shift portion as reaction elements; a clutch means for selectively transmitting power to operational elements of the primary shift portion; and a non-synchronous shift means for operating during 1 ⁇ 2, 2 ⁇ 3 and 4 ⁇ 2 shifting.
  • the secondary shift portion is a second planetary gearset, a ring gear of which is fixedly connected to the output shaft.
  • the power transmitting means comprises a first power transmitting gear connected to a planet carrier of the first planetary gearset; a second power transmitting gear meshed with the first power transmitting gear, and connected to the ring gear of the second planetary gearset and the output shaft; a third power transmitting gear provided on the first shaft and fixedly connected to the sun gear of the first planetary gearset; and a fourth power transmitting gear meshed with the third power transmitting gear, fixedly connected to a sun gear of the second planetary gearset, and provided on the second shaft.
  • the brake means comprises a first brake provided between the second shaft and a transmission housing; a second brake provided between the first shaft and the transmission housing with elements of the non-synchronous shift means being interposed between the second brake and the first shaft; and a third brake provided between the first shaft and the transmission housing.
  • the clutch means comprises a first clutch selectively connecting the ring gear of the first planetary gearset and the input shaft; a second clutch selectively connecting the sun gear of the first planetary gearset and the input shaft; and a third clutch selectively connecting a sun gear and a planet carrier of the second planetary gearset.
  • the non-synchronous shift means comprises a first one-way clutch interposed between the second shaft and the transmission housing, the first one-way clutch operating in a first speed to enable an element of the second planetary gearset to act as a reaction element; and a second one-way clutch interposed between the first shaft and the second brake, the second one-way clutch operating in a second speed to enable an element of the first planetary gearset to act as a reaction element during operation of the second brake.
  • FIG. 1 is a schematic diagram of a powertrain according to a preferred embodiment of the present invention
  • FIG. 2 is an operational chart of friction elements in each shift range of the powertrain shown in FIG. 1;
  • FIG. 3 is a lever analogy used to describe the operation of the powertrain of FIG. 2 in a first speed of a drive D range;
  • FIG. 4 is a lever analogy used to describe the operation of the powertrain of FIG. 2 in a second speed of the drive D range;
  • FIG. 5 is a lever analogy used to describe the operation of the powertrain of FIG. 2 in a third speed of the drive D range;
  • FIG. 6 is a lever analogy used to describe the operation of the powertrain of FIG. 2 in a fourth speed of the drive D range;
  • FIG. 7 is a lever analogy used to describe the operation of the powertrain of FIG. 2 in a reverse R range.
  • FIG. 1 shows a schematic diagram of a powertrain according to a preferred embodiment of the present invention.
  • the torque converter T includes a pump impeller PI directly linked to the crankshaft of the engine E to rotate with the crankshaft; a turbine runner TR provided opposing the pump impeller PI and rotating as a result of a fluid (e.g., oil) expelled from the pump impeller PI; and a stator ST disposed between the pump impeller PI and the turbine runner TR, the stator ST changing a flow direction of the fluid to increase a rotational force of the pump impeller PI.
  • a fluid e.g., oil
  • the pump impeller PI begins to rotate such that the fluid in the torque converter T is expelled from the pump impeller PI and supplied to the turbine runner TR to drive the turbine runner TR.
  • the fluid then flows to the stator ST which changes the flow direction of the fluid and supplies it back to the pump impeller PI.
  • the torque converter T acts as a torque multiplier.
  • the first planetary gearset 1 which receives power from the torque converter T, is provided on a first shaft 23 , the first shaft 23 being on an identical axis as an input shaft 5 (i.e., aligned with the input shaft 5 ).
  • the second planetary gearset 3 is provided on a second shaft 25 , the second shaft 25 being spaced at a predetermined interval from and parallel to the first shaft 23 .
  • the first and second planetary gearsets 1 and 3 acting respectively as primary and secondary shift portions as described above, are interconnected as will be described below.
  • the first planetary gearset 1 is mounted on the first shaft 23 through a sun gear 11 .
  • the second planetary gearset 3 is mounted on the second shaft 25 through a planet carrier 19 , parallel to the first planetary gearset 1 , and at a predetermined distance from the same.
  • the first and second planetary gearsets 1 and 3 are interconnected by a separate power transmitting means.
  • the aforementioned power transmitting means includes (a) a first power transmitting gear 27 fixedly connected to a planet carrier 13 of the first planetary gearset 1 such that the first power transmitting gear 27 is able to rotate on the first shaft 23 , and (b) a second power transmitting gear 29 fixedly connected to both a ring gear 21 of the second planetary gearset 3 and an output shaft 31 such that the second power transmitting gear 29 is able to rotate on the second shaft 25 .
  • the first power transmitting gear 27 is meshed with the second power transmitting gear 29 .
  • a third power transmitting gear 33 which is fixedly connected to the sun gear 11 of the first planetary gearset 1 through the first shaft 23 , is meshed with a fourth power transmitting gear 35 , the fourth power transmitting gear 35 being fixedly connected to a sun gear 17 of the second planetary gearset 3 such that the fourth power transmitting gear 35 is able to rotate on the second shaft 25 .
  • the first and second planetary gearsets 1 and 3 interconnected as described above are provided respectively on the input shaft 5 and the output shaft 31 , and on the first shaft 23 and the second shaft 25 , in such a manner that the rotation of the first planetary gearset 1 does not interfere with that of the second planetary gearset 3 .
  • the first and second planetary gearsets 1 and 3 are also connected to brakes, clutches and non-synchronous shift means.
  • a ring gear 15 of the first planetary gearset 1 is connected to the input shaft 5 with a first clutch C 1 interposed therebetween. Also, one end of the sun gear 11 of the first planetary gearset 1 is connected to the input shaft 5 with a second clutch C 2 interposed therebetween, and its other end is connected through the first shaft 23 to a transmission housing 37 with a second brake B 2 and a second one-way clutch F 2 interposed therebetween, and separately with a third brake B 3 interposed therebetween.
  • the second one-way clutch F 2 is provided between the second brake B 2 and the first shaft 23 .
  • the planet carrier 19 of the second planetary gearset 3 is connected to the transmission housing 37 through the second shaft 25 with a first brake B 1 interposed therebetween, and separately to the transmission housing 37 through the second shaft 25 with a first one-way clutch F 1 interposed therebetween.
  • the planet carrier 19 still operates with a reverse rotation of the second shaft 25 .
  • the planet carrier 19 of the second planetary gearset 3 is connected through the second shaft 25 to the sun gear 17 of the second planetary gearset 3 with a third clutch C 3 interposed therebetween. Accordingly, the second planetary gearset 3 operates as an integral device.
  • Shifting is realized by the selective operation of the friction elements in the powertrain of the present invention as shown in the chart of FIG. 2 . Together with the lever analogy of FIG. 3, the shifting operation of the present invention will be described in more detail hereinbelow.
  • a first node N 1 of a first lever Lever 1 represents the sun gear 11 of the first single pinion planetary gearset 1
  • a second node N 2 of the first lever Lever 1 represents the planet carrier 13 of the first planetary gearset 1
  • a third node N 3 of the first lever Lever 1 represents the ring gear 15 of the first planetary gearset 1
  • a fourth node N 4 of a second lever Lever 2 represents the sun gear 17 of the second planetary gearset 3
  • a fifth node N 5 of the second lever Lever 2 represents the planet carrier 19 of the second planetary gearset 3
  • a sixth node N 5 of the second lever Lever 2 represents the ring gear 21 of the second planetary gearset 3 .
  • the elements represented by the nodes are determined by the combination of the planetary gearsets. Since this is well known in the art, a detailed description thereof will be omitted.
  • the first clutch C 1 In a first speed of a drive D range, the first clutch C 1 is engaged. Accordingly, the rotation of the input shaft 5 , which receives power from the engine E, is transmitted to the ring gear 15 of the first planetary gearset 1 such that the ring gear 15 acts as an input element.
  • the planet carrier 13 of the first planetary gearset 1 In this first speed operation, the planet carrier 13 of the first planetary gearset 1 is connected to deliver output to the road surface through the first and second power transmission gears 27 and 29 and through the ring gear 21 of the second planetary gearset 3 . In this state, the planet carrier 13 of the first planetary gearset 1 operates as a reaction element until the vehicle begins its forward motion.
  • a rotational direction of the planet carrier 13 as well as of the sun gear 11 of the first planetary gearset 1 is determined such that the planet carrier 13 rotates in a forward direction while the sun gear 11 rotates in a reverse direction.
  • the sun gear 17 of the second planetary gearset 3 receives rotational power from the third power transmitting gear 33 after the rotational power is reduced through the fourth power transmitting gear 35 .
  • the third power transmitting gear 33 is connected to the ring gear 15 of the first planetary gearset 1 through the sun gear 11 of the first planetary gearset 1 and the first shaft 23 .
  • the planet carrier 19 of the second planetary gearset 3 attempts to rotate in the reverse direction as a result of a rotational ratio of the sun gear 17 and the ring gear 21 of the second planetary gearset 3 .
  • the rotation of the planet carrier 19 is repressed such that the planet carrier 19 operates as a reaction element.
  • the ring gear 15 of the first planetary gearset 1 becomes an input element, and the planet carrier 19 of the second planetary gearset 3 acts as a reaction element, thereby realizing shifting into the first speed of the drive D range. Further, output is realized through the ring gear 21 of the second planetary gearset 3 .
  • first and second output speed lines D 1 S 1 and D 1 Ca 1 output respectively through the first and second nodes N 1 and N 2 of the first lever Lever 1 , are determined.
  • the first and second output speed lines D 1 S 1 and D 1 Ca 1 are formed not only by the operation of the first planetary gearset 1 , but are related also to the operation elements of the second planetary gearset 3 . This is realized by linkages through the first, second, third and fourth power transmitting gears 27 , 29 , 33 and 35 .
  • the first output speed line D 1 S 1 is reduced through the third and fourth power transmitting gears 33 and 35 , and transmitted to the fourth node N 4 of the second lever Lever 2 , similar to a second input speed line D 1 S 2 .
  • the sixth node N 6 is connected to the second output speed line D 1 Ca 1 extending from the second node N 2 of the first lever Lever 1 . That is, input is realized through the ring gear 15 of the first planetary gearset 1 , and with the planet carrier 19 of the second planetary gearset 3 acting as a reaction element, a first speed output speed line D 1 like that of a third output speed line D 1 R 2 of the second lever Lever 2 , which is output through the ring gear 21 of the second planetary gearset 3 , is realized.
  • a transmission control unit performs control to engage the second brake B 2 .
  • the second one-way clutch F 2 is engaged such that the sun gear 11 of the first planetary gearset 1 operates as a reaction element.
  • the sun gear 17 of the second planetary gearset 3 also operates as a reaction element such that the rotational force generated from the planet carrier 13 of the first planetary gearset 1 is transmitted directly to the output shaft 31 by the first and second power transmitting gears 27 and 29 , thereby realizing shifting into a second speed of the drive D range.
  • the first output speed line D 2 Ca 1 is transmitted directly as output rpm to the sixth node N 6 of the second lever Lever 2 to determine a second output speed line D 2 R 2 .
  • a second speed output line D 2 like that of the second output speed line D 2 R 2 of the second lever Lever 2 , which is output through the ring gear 21 of the second planetary gearset 3 , is realized. Accordingly, the second speed output line D 2 has a greater output rpm than the first speed output line D 1 .
  • the TCU performs control to engage the second clutch C 2 .
  • rotational power is directly transmitted to the ring gear 21 of the second planetary gearset 3 through the first and second power transmitting gears 27 and 29 , to be transmitted to the output shaft 31 . Also, through the third and fourth power transmitting gears 33 and 35 , the rotational power is reduced then transmitted to the sun gear 17 of the second planetary gearset 3 . The difference in rotational speeds is absorbed by the planet carrier 19 of the second planetary gearset 3 rotating in reverse. Accordingly, shifting into a third speed of the drive D range is realized.
  • a line connecting the second node N 2 to a line L 3 which connects a first input line D 3 S 1 input to the first node N 1 of the first lever Lever 1 to a second input line D 3 R 1 of the third node N 3 of the first lever Lever 1 , becomes a first output speed line D 3 Ca 1 .
  • the first output speed line D 3 Ca 1 is transmitted to the sixth node N 6 of the second lever Lever 2 through the first and second power transmitting gears 27 and 29 to determine a second output speed line D 3 R 2 .
  • the TCU performs control to disengage the second clutch C 2 and engage the third clutch C 3 . Accordingly, input through the sun gear 11 of the first planetary gearset 1 is discontinued, and the sun gear 17 and planet carrier 19 of the second planetary gearset 3 are integrally fixed.
  • the second planetary gearset 3 operates as an external input element through the first, second, third and fourth power transmitting gears 27 , 29 , 33 and 35 such that rpm of the planet carrier 13 , corresponding to the rpm of rotational power input through the ring gear 15 at a particular point, is determined, thereby realizing shifting into a fourth speed of the drive D range through the ring gear 21 of the second planetary gearset 3 .
  • a third output speed line D 4 R 2 of the second lever Lever 2 is determined from the sixth node N 6 .
  • the third output speed line D 4 R 2 is linked to the ring gear 21 of the second planetary gearset 3 .
  • overdrive is realized in which a faster output than that of the fourth speed of the drive D range results.
  • the input through the sun gear 11 of the first planetary gearset 3 is reduced through the sun gear 17 of the second planetary gearset 3 via the third and fourth power transmitting gears 33 and 35 , and the second planetary gearset 3 operates such that the planet carrier 19 acts as a reaction element and output is realized through the ring gear 21 .
  • a first input speed line RS 1 input to the first node N 1 of the first lever Lever 1 , is reduced at the fourth node N 4 of the second lever Lever 2 and transmitted to a second input speed line RS 2 .
  • a first output speed line RR 2 extending from the sixth node of the second lever Lever 2 is determined by a line L 5 , which extends using the fifth node N 5 of the second lever Lever 2 as a reaction element.
  • the length of the powertrain is minimized and the overall structure is simplified. Also, with the use of a one-way clutch for 1 ⁇ 2, 2 ⁇ 3 and 4 ⁇ 2 shifting, shift feel is greatly improved.

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  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
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US09/610,898 1999-11-09 2000-07-06 Automatic transmission powertrain Expired - Fee Related US6394928B1 (en)

Applications Claiming Priority (2)

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KR1019990049403A KR100337350B1 (ko) 1999-11-09 1999-11-09 자동 변속기용 파워 트레인
KR99-49403 1999-11-09

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US (1) US6394928B1 (zh)
JP (1) JP4215185B2 (zh)
KR (1) KR100337350B1 (zh)
CN (1) CN1136108C (zh)
AU (1) AU763634B2 (zh)
DE (1) DE10033476B9 (zh)

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CN101473147B (zh) * 2006-06-23 2012-12-12 腓特烈斯港齿轮工厂股份公司 双离合器变速箱
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KR101145625B1 (ko) 2009-11-23 2012-06-28 현대자동차주식회사 토크 분기형 자동변속기
KR101509677B1 (ko) 2009-11-23 2015-04-08 현대자동차 주식회사 토크 분기형 자동변속기
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CN115013520B (zh) * 2022-06-17 2024-05-17 潍柴动力股份有限公司 Amt变速箱中间轴制动控制方法、装置及控制器

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Publication number Priority date Publication date Assignee Title
CN101473147B (zh) * 2006-06-23 2012-12-12 腓特烈斯港齿轮工厂股份公司 双离合器变速箱
CN102644707A (zh) * 2011-02-17 2012-08-22 通用汽车环球科技运作有限责任公司 具有带式制动器的多档变速器
US10753432B2 (en) * 2018-06-14 2020-08-25 Hyundai Motor Company Power transmission apparatus for vehicle

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CN1136108C (zh) 2004-01-28
DE10033476B9 (de) 2006-01-12
JP2001140999A (ja) 2001-05-22
KR20010045891A (ko) 2001-06-05
DE10033476A1 (de) 2001-05-10
AU4380200A (en) 2001-05-10
CN1294991A (zh) 2001-05-16
JP4215185B2 (ja) 2009-01-28
DE10033476B4 (de) 2005-08-04
KR100337350B1 (ko) 2002-05-21
AU763634B2 (en) 2003-07-31

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